EP0576789B1 - Flüssigkeitsreibungskupplung - Google Patents

Flüssigkeitsreibungskupplung Download PDF

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Publication number
EP0576789B1
EP0576789B1 EP93105024A EP93105024A EP0576789B1 EP 0576789 B1 EP0576789 B1 EP 0576789B1 EP 93105024 A EP93105024 A EP 93105024A EP 93105024 A EP93105024 A EP 93105024A EP 0576789 B1 EP0576789 B1 EP 0576789B1
Authority
EP
European Patent Office
Prior art keywords
valve
fluid friction
differential pressure
friction coupling
coupling according
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP93105024A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0576789A2 (de
EP0576789A3 (enrdf_load_stackoverflow
Inventor
Hans Dipl.-Ing. Martin
Werner Hummel
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mahle Behr GmbH and Co KG
Original Assignee
Behr GmbH and Co KG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Behr GmbH and Co KG filed Critical Behr GmbH and Co KG
Publication of EP0576789A2 publication Critical patent/EP0576789A2/de
Publication of EP0576789A3 publication Critical patent/EP0576789A3/xx
Application granted granted Critical
Publication of EP0576789B1 publication Critical patent/EP0576789B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D35/00—Fluid clutches in which the clutching is predominantly obtained by fluid adhesion
    • F16D35/02—Fluid clutches in which the clutching is predominantly obtained by fluid adhesion with rotary working chambers and rotary reservoirs, e.g. in one coupling part
    • F16D35/021—Fluid clutches in which the clutching is predominantly obtained by fluid adhesion with rotary working chambers and rotary reservoirs, e.g. in one coupling part actuated by valves
    • F16D35/022—Fluid clutches in which the clutching is predominantly obtained by fluid adhesion with rotary working chambers and rotary reservoirs, e.g. in one coupling part actuated by valves the valve being actuated by a bimetallic strip

Definitions

  • the invention relates to a fluid friction clutch according to the preamble of claim 1, as is known for example from DE-C 28 14 608.
  • a fluid friction clutch with a centrifugal valve is known, which is arranged in the return channel between the working and storage chamber and opens the return channel depending on the output speed of the clutch.
  • the return channel is therefore closed at a standstill, so that there is no flow connection between the working chamber and the storage chamber.
  • a known fluid friction clutch according to DE-A 32 42 381 is constructed similarly, a check valve being provided in the return flow channel (pump channel) between the working and storage chamber according to FIG. 5, which is not dependent on the centrifugal force but on the excess pressure between the working and storage chamber is working.
  • This check valve is designed as a plastic flap and only allows the direction of flow from the working chamber into the storage chamber and not vice versa. This plastic valve is temperature-dependent with regard to its elastic properties.
  • the object of the present invention is therefore to increase the idle speed by simple measures in generic clutches and to stabilize this idling speed if possible also at a defined speed level.
  • This object is achieved by the characterizing features of claim 1, ie by a so-called differential pressure valve in the return flow channel of the clutch.
  • This measure is based on the knowledge that an increase in the idle speed can be achieved by increasing the static pressure in the storage room. This is done by using the differential pressure valve according to the invention, the opening pressure of which is added to the static pressure in the storage chamber. As a result, less oil flows from the working chamber into the storage chamber, and the degree of filling in the working chamber increases, and consequently also the idling speed. Since the opening pressure can be set in such a differential pressure valve, for example by selecting a suitable return spring, the level of the desired idling speed can also be determined.
  • the differential pressure valve can be designed as a check valve or as a spring-loaded ball valve, which is arranged either in the radial or axial part of the return flow channel between the working chamber and the storage chamber.
  • a check valve or as a spring-loaded ball valve, which is arranged either in the radial or axial part of the return flow channel between the working chamber and the storage chamber.
  • the differential pressure valve is accessible from the outside, so that it can also be replaced. It is also advantageous if the valve is designed as an insert cartridge which can be inserted into a standard bore in the clutch housing. This allows different valve types with different opening pressures to be installed and subsequently exchanged with a uniform design of the clutch housing.
  • Fig. 1 shows in section a fluid friction clutch, as it is used for cooling internal combustion engines in motor vehicles as a fan clutch.
  • This fluid friction clutch is driven on its drive side, which is formed by a drive shaft 2 and a drive pulley 1, by the internal combustion engine directly or via a V-belt drive.
  • the output takes place via a clutch housing 3, which has a working chamber 4 and a storage chamber 5, which are separated from one another by a partition 6.
  • a viscous medium silicone oil
  • a valve opening 7 which is controlled by a valve lever 8 which in turn is controlled by means of a switching pin 9 via a bimetal 10 arranged on the outside.
  • a return flow channel which is formed from an axially extending part 13a and a radially extending part 13b and thus establishes a connection between the working chamber 4 and the storage chamber 5.
  • a bluff body 16 is arranged in the area of the inlet opening of the return flow channel 13a, which ensures the return of the viscous medium from the working chamber 4 to the storage chamber 5.
  • the inflow of the viscous medium takes place via the valve opening 7, so that there is a circulation of the viscous medium between the storage chamber 5 and the working chamber 4 when the valve 7, 8 is open - as indicated by the two arrows.
  • the clutch housing 3 carries a fan blading 12 and is rotatably mounted on the drive shaft 2 via the roller bearing 11.
  • a differential pressure valve which consists of a ball 14 and a spiral spring 15 which is supported on the one hand in the return flow channel 13b by a shoulder 13c and on the other hand presses the ball 14 against a conical seat , which is formed by a valve insert 13d.
  • This has cross-shaped bores which are connected on the one hand to the radially extending part 13b and on the other hand to the axially extending part 13a of the return flow channel.
  • FIG. 2 shows a further embodiment variant of the differential pressure valve in an enlarged section of the clutch, the drive disk 21 of which forms working gaps 22, 23 with the housing walls.
  • a bluff body 26 is arranged radially outside, ie on the circumferential side of the drive disk 21, in the region of which the opening of the axially extending return flow channel 27 is located.
  • This part of the return flow channel 27 is followed, on the one hand, by a radially extending part 28 of the return flow channel, which leads to the storage chamber (not shown), and on the other hand by an axially extending, enlarged diameter valve bore 29, which is sealed to the outside by a closure 30.
  • valve spring 31 Within this valve bore 29 there is a valve ball 32, which is pressed by a valve spring 31 against a conical seat which opens into the return flow channel 27.
  • the valve spring 31 can therefore be easily inserted from the outside into the bore 29 and consequently can also be easily exchanged for another spring.
  • the clutch does not engage - the cause of the static pressure in the reservoir is too low because the idle speed is too low, as this determines the static pressure in the reservoir due to centrifugal force.
  • the differential pressure valve according to the invention "artificially" increases the static pressure in the storage space, because the pressure in the return flow channel 13a or 27 caused by the closed valve is added to the static pressure in the storage chamber 5 or in the radially extending part of the return flow channel 13b or 28.
  • the bluff body 16 or 26 in the working chamber must deliver against a higher pressure when the differential pressure valve is closed, as a result of which more oil builds up in the working space, the degree of filling increases and the idling speed increases.
  • the differential pressure valve also has the advantage that the level of the idling speed can be set precisely by the choice of the restoring force of the valve, that is to say by means of a suitable spring force of the valve spring, or can also be replaced if necessary.
  • the relationship here is that the higher the spring force of the valve spring in the differential pressure valve, the higher the idling speed. This means that the idle speed can be set precisely or corrected either before installing the clutch or after installing it.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
  • Safety Valves (AREA)
  • Multiple-Way Valves (AREA)
EP93105024A 1992-06-30 1993-03-26 Flüssigkeitsreibungskupplung Expired - Lifetime EP0576789B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4221450A DE4221450A1 (de) 1992-06-30 1992-06-30 Flüssigkeitsreibungskupplung
DE4221450 1992-06-30

Publications (3)

Publication Number Publication Date
EP0576789A2 EP0576789A2 (de) 1994-01-05
EP0576789A3 EP0576789A3 (enrdf_load_stackoverflow) 1994-04-20
EP0576789B1 true EP0576789B1 (de) 1997-08-06

Family

ID=6462154

Family Applications (1)

Application Number Title Priority Date Filing Date
EP93105024A Expired - Lifetime EP0576789B1 (de) 1992-06-30 1993-03-26 Flüssigkeitsreibungskupplung

Country Status (4)

Country Link
US (1) US5404977A (enrdf_load_stackoverflow)
EP (1) EP0576789B1 (enrdf_load_stackoverflow)
DE (2) DE4221450A1 (enrdf_load_stackoverflow)
ES (1) ES2106214T3 (enrdf_load_stackoverflow)

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0743503U (ja) * 1993-12-30 1995-08-22 株式会社ユニシアジェックス 流体継手
JPH08296669A (ja) * 1995-04-27 1996-11-12 Usui Internatl Ind Co Ltd 流体式ファン・カップリング装置
DE19623676C1 (de) * 1996-06-14 1997-07-03 Fichtel & Sachs Ag Klimaanlage mit einem Kältekompressor mit Visko-Kupplung
US5975265A (en) * 1998-06-24 1999-11-02 Behr America, Inc. Fabrication of fluid coupling
US7600623B1 (en) 2006-02-06 2009-10-13 Standard Motor Products Inclusion of an anti-drain valve in viscous fan clutches
US20080217132A1 (en) * 2007-03-07 2008-09-11 Aisin Seiki Kabushiki Kaisha Viscous Fluid Coupling Device
EP2867487A4 (en) * 2012-06-27 2016-04-27 Borgwarner Inc VISCOUS FAN DRIVING SYSTEMS WITH FAN DRIVING SLIDE RETURN
DE102018216479A1 (de) * 2018-09-26 2020-03-26 Mahle International Gmbh Flüssigkeitsreibkupplung

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2792095A (en) * 1955-11-30 1957-05-14 Motor Products Corp Constant torque pulley
US3259220A (en) * 1964-02-25 1966-07-05 Eaton Mfg Co Rotatable coupling
JPS5493760A (en) * 1978-01-07 1979-07-25 Toyota Motor Corp Fluid coupling
DE3122958A1 (de) * 1981-06-10 1983-01-05 Fichtel & Sachs Ag, 8720 Schweinfurt Viskose-luefterkupplung mit rueckschlagventil
DE3242381C2 (de) * 1981-11-30 1986-05-28 Aisin Seiki K.K., Kariya, Aichi Flüssigkeitsreibungskupplung
JPS5934030A (ja) * 1982-07-12 1984-02-24 Aisin Seiki Co Ltd 温度感応型粘性流体継手
JPS59190521A (ja) * 1983-04-14 1984-10-29 Aisin Seiki Co Ltd 粘性流体継手
US4924987A (en) * 1989-05-22 1990-05-15 General Motors Corporation Pump plate assembly for a viscous fluid clutch
US4995494A (en) * 1989-05-22 1991-02-26 General Motors Corporation Pressure-responsive fluid check valve and method for viscous fluid clutch

Also Published As

Publication number Publication date
US5404977A (en) 1995-04-11
EP0576789A2 (de) 1994-01-05
DE59307054D1 (de) 1997-09-11
DE4221450A1 (de) 1994-01-05
ES2106214T3 (es) 1997-11-01
EP0576789A3 (enrdf_load_stackoverflow) 1994-04-20

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